Rotary-linear dual-directional rotating actuator

ABSTRACT

A ROTARY-LINE ACTUATOR TO PERMIT RETRUCTION OF A CUTTING TOOL IN A BORING AND SIZE COMPENSATION OF THE CUTTING TOOL IN EITHER CLOCKWISE OR COUNTERCLOCKWISE DIRECTION.

NOV. 16, 1971 J, N|TK|EW|CZ ETAL 3,62,13

ROTARY-LINEAR DUAL-DIREGTIONAL ROT/WING ACTUATOR Filed Dec. 4, 1969 3Shoots-Shoot il.

A T TORNE V NOV. 16, 1971 J N|TK|EW1CZ EI'AL 3,620,13

ROTARY-LINEAR DUAL-DIRECTIONAL ROTATING ACTUATOR Filed Dec. 4, 1969 3Shoots-Shoot 2 jm A/.m

A 7' TORNEV Nov. 16, 1971 J. NITKIEWICZ ET AL I5 Shoots-Shoot 5 WMA/.

ATTORNEY United States Patent Oce 3,620,131 ROTARY-LINEARDUAL-DIRECTIONAL ROTATING ACTUATOR c Joseph Nitkiewicz, Farmington, andNathan Mendelsohn,

Oak Park, Mich., assignors to Ex-Cell-O Corporation,

Detroit, Mich.

Filed Dec. 4, 1969, Ser. No. 881,973 Int. Cl. F01b 21/00 U.S. Cl. 92-2 1Claim ABSTRACT OF THE DISCLOSURE A rotary-linear actuator to permitretraction of la cuttlng. tool 1n a boring bar and size compensation ofthe cutting tool in either clockwise or counterclockwise direction.

BACKGROUND OF THE INVENTION (1) Field of the invention This inventionrelates to an improved version of tluid control devices of the typeshown in Drake Pat. No. 3,215,046, issued Nov. 2, 1965, and Ludwig etal. Pat. No. 2,793,623, issued May 28, 1957, in which a plurality ofcircumferentially disposed vanes mounted on a shaft are partiallyrotated by hydraulic fluid to selectively rotate the shaft inincrements. As shown in Griswold et al., Pat. No. 3,391,585, issued July9, 1968, on a Boring Spindle, the intermittent rotary motion of theactuator causes a rotary index of the cam which is mounted to anactuating bar yand which action changes tool size. This inventioncombines the rotary fluid control and the rotary indexing of the cam andis particularly concerned with the linear and/or rotary movement of theactuating bar in either clockwise or counterclockwise direction.

(2) Description of the prior art It is known to selectively hold andrelease a shaft by means of devices utilizing a releasing means. Thesereleasing means may comprise electromagnetic clutches, pressure rollers,or vane type such as disclosed in the above noted patents. Moreover, inthe copending patent application, S.N. 861,109, filed Sept. 25, 1969 ona Rotary- Linear Actuator is directed to a single direction.

SUMMARY OF THE INVENTION According to the present invention, a rotatingrotary actuator and piston are mounted to a rotatable spindle andconnected to a hydraulic pressure source through a rotary coupling.Piston actuation causes the actuating bar to move in a linear directionthereby causing the connected tapered cam to retract the cutting tool. Adual directional clutch means permits dual direction rotary motion of acam which action changes tool size, either during spindle rotation orwhen the spindle is not rotating.

BRIEF DESCRIPTION OF THE DRAWINGS FIG. 1 is partial cross-sectional viewof the rotary actuator assembly, and taken along line 1-1 of FIG. 2.;

FIG. 2 is partial cross-sectional view of the rotary vane means, andtaken along a line 2-2 of FIG. 1;

FIG. 3 is an end view of the rotary linear actuator;

FIG. 4 is a schematic diagram showing one of the arrangements forsupplying the liuid, air or hydraulic, to the actuators.

DESCRIPTION OF THE PREFERRED EMBODIMENT The cutting tool of a precisionboring spindle requires a means for retracting the tool after the boringoperation has been finished in order to avoid tool marks during thereturn stroke of the spindle. It is also desirable to provide 3,620,131Patented Nov. 16, 1971 a means for a controlled bidirectional radialmotion 0f the cutting tool in order to compensate for the wear of thetool, or adjust for size, thus holding the part dimensions within thedesired size or tolerance limits.

The purpose of the following described invention is to provide a compactrotating unit capable of providing both the retract as well as thebidirectional compensating motions as described in the foregoing. Thecompensating and retracting motions are accomplished during spindlerotation at normal operating speeds. This rotating retracting andbidirectional compensating unit Will also operate when the spindlerotation is stationary. It is intended for any application requiringcontrolled linear and rotational motion of any practical length and/orspecific rotary movement within one full revolution such as the devicepatented in Griswold et al. Pat. No. 3,391,585, and in copending patentapplication S.N. 861,109, liled on Sept. 25, 1969.

Referring to FIG. 1, the actuator assembly 10 is shown in the positionit is mounted to the pulley 11 of a precision boring spindle.

The embodiment of the actuator assembly 10 is comprised of a rotaryactuator unit 13, a body 15, a manifold 17, a rotary union 19, a firsttoothed clutch means 21, and actuating or draw bar 23, and a secondtoothed clutch means 25.

On the right end of the body 15, a flange 27 is secured thereto by bolts28, and with the use of bolts 29 serves as a means of mounting thecomplete assembly to the pulley 11, and, at the same time, provides acoaxial alignment with the spindle. A sleeve 31 connected to vanes 69and 71 axially receives actuating bar 23 (this is element 27 incopending patent application S. N. 861,109, filed on Sept. 25, 1969 inthe name of Joseph Nitkiewicz; assigned to the assignee of record).

The actuating bar 23 includes splines 35 on the end thereof, which coactwith internal splines 39 on piston 37, for reasons to be explainedherein.

The rotary actuator assembly unit 13 is mounted for rotary movementonly. That is, vanes 69 and 71 are connected to the sleeve 31 andtoothed clutch teeth 43 are circumferentially arranged on the internalend of said sleeve 31.

When the rotary actuator assembly 13 is indexed either clockwise orcounterclookwise, the toothed clutch teeth 43 on the sleeve 31 isadapted to engage toothed clutch teeth 45 on piston 37 by movement ofthe piston 37 toward the right, as in FIG. 1. The piston movement iselected by movement of iluid in passage 47 of rotatable shaft 49 inrotary union 19. The shaft 49 is rotating with the actuator assembly 10,while the rotary union 19 is stationary, thus allowing stationary fluidsupply and drain lines to be connected to the ports 50, 51, and 52. Theliuid is transmitted by means of fluid channels 47, 53, and 55 tooperate the rotary-linear actuator means. The rotary motion isaccomplished as follows: fluid flows in passages 57 and 59 in manifold17, through channels 61 and 63 of body 15 and enters the chambers 65 and67, respectively, of the rotary actuator unit 13. Depending on thedirection required, vanes 69 and 7'1 will move in increments of 730, seeFIG. 4. Since this is a closed system, while one side of the vane isbeing moved by the liuid, either clockwise or counterclockwise, thefluid on the other side of the vane is being drained to reservoir 93.The piston 37 is adapted for forward or retract motion, as well asrotational motion. That is, the forward and retract motion of the piston37 is to provide the ton'king feature, as disclosed in the above notedlGriswold et al. patent. However, the piston has an additional featurein that it provides the rotational movement of the actuating barnecessary for compensation of the cutting tool. This is accomplishedwhen the piston 37 is moved toward the right,

as in FIG. 1, causing toothed clutch teeth 45 on piston 37 to engage thetoothed clutch teeth 43 on sleeve 31. Movement of the vanes 69 and 71,either clockwise or counterclockwise effects movement of sleeve 31.Axial movement of piston 37 engages first toothed clutch means 21. Thusrotational movement of sleeve 31 causes rotational movement of piston 37and through splines 35, 39 causes rotational movement to actuating bar23, and rotation of actuating bar 23 will result in indexing the cuttingtool in a manner disclosed in the Griswold et al. patent; i.e., movingthe cutting tool to a new position to compensate `for wear on thecutting tool, or to adjust the tool for different bore sizes. The splineconnection between the actuating bar 23 and piston 37 ensures a positivetorque transmitting capability. The toothed clutch teeth 45 on piston 37must be engaged with the toothed clutch teeth 43 on sleeve 31 whenever acompensating type of rotary motion is desired; however, it must bedisengaged when the rotary actuator is being reset for the next desiredindexing cycle. Therefore, each indexing type of motion is accomplishedin three steps: the first step is to engage the toothed clutch teeth 43and 45; i.e., engage the first clutch means 21; the second step is toperform the compensating type of rotary motion, either clockwise orcounterclockwise; and finally to disengage the first clutch means 21 toreset the rotary actuator for the next compensatory cycle.

When the piston is moved to its most rearward position, or left as shownin FIG. 1, the toothed clutch teeth 73 on the other side of piston 37,contacts the toothed clutch teeth 75 on adjusting bushing 16 which isabutting manifold 17. The manifold 17, adjusting bushing 16, body 15,and fiange 27 comprise the integral actuator assembly unit 10, which isconnected to pulley 11. As the pulley 11 rotates the actuator assemblyunit 10, the rotational movement is imparted to the shaft 23, throughthe second clutch means 25 and splines 35, and 39 effects coordinatedrotation of the cutting tool and actuating bar.

OPERATION (A) Retract FIG. 4 shows a schematic representation of theinvention. Valves 89 and 91 are two-position spring-offset directionalvalves, which can be shifted in either one of positions A or B. Whenboth directional valves 89 and 91 are in position A, as shown, bothfiuid passages 47 and 55 are connected to reservoir 93. The linearactuator is in the normal position; and the rotary actuator ispositively retained against stop 105 through positive fluid pressure influid passage 53. Consequently, the cutter is in its normal working orcutting position. By energizing the right side of valve 91, the spool isshifted to position B, and fiuid under pressure is being supplied toport 50, through channel 47 in rotatable shaft 49 of coupling 19, toforward face area 95 of piston 37, causing piston 37 to move forward.Moving piston 37 forward pushes the actuating bar 23 and consequentlyretracts the cutter radially. The cutter will be kept in this retractedposition until it is removed from the bore or other structuralobstructions of the workpiece. Deenergizing valve 91 moves thespringoffset spool back to position A thereby connecting line 47 toreservoir. The piston 37 will return to the normal position through theforce of the spring 97 acting on returning actuating bar 23.

(B) Rotary motion Energizing valve 89, the spool will be shifted toposition B and fiuid under pressure will be supplied to port 52, throughchannels 55, 59, and 61 to one side of vanes 69 and 71. The pressurizedfluid will force the vane 69 to rotate until it reaches a stop 77signifying a partial movement of a preset amount. The rotary actuator isnow set for a counterclockwise indexing motion. The piston 37 must beengaged with the rotary actuator sleeve 31 whenever a compensating typerotary motion of the draw bar 23 is necessary, and it must be disengagedwhen the rotary actuator is being reset for the next indexing cycle.Consequently, valve 91 is energized, thereby shifting its spool toposition B, allowing fluid under pressure to flow through channel 47 ofrotatable shaft 49 to forward area 95 of piston 37, causing the piston37 to move forward thereby retracting the cutter and engaging firsttoothed clutch means 21; that is, allowing the toothed clutch teeth 45to engage the toothed clutch teeth 43 on the rotary actuaor sleeve 31.With the piston 37 in the forward direction, and toothed clutch means 21engaged, valve 89 is deenergized, allowing the spool to lbe shifted toposition A. Consequently, uid in chamber 67 will now be connected. tothe reservoir 93, and the other side of vanes 69 and 71 is supplied bypressurized fluid by way of port 51, channels 53, 57, and 63 to rotatevanes 69 and 71. Rotation of vanes 69 and 71 is for compensatingactuating bar 23 through rotary actuator sleeve 31, Ifirst toothedclutch means 21, piston 37, and splines 35, 39. This rotation is thustransformed into a radial motion of the cutter as required to compensatefor wear of the tool, or to adjust for varied bore sizes.

Deenergizing valve 91 allows the spool to shift back to position A,connecting channel 47 to reservoir, thus causing piston 37 to return toits normal position, through the force of spring 97 acting on actuatingbar 23. At the same time that the toothed clutch teeth 43 and 45 aredisengaged, the tool cutter is expanded to the new compensated oradjusted radial position.

For rotary compensating motion in a clockwise direction the following isapplied. The vane 69 resting on stop 105, is already set for a clockwisecompensating motion, therefore, no resetting cycle is necessary. Valve91 is energized, allowing the piston 37 to move forward and engagetoothed clutch teeth 43 and 45. Then the valve 89 is energized allowingfiuid under pressure to fiow to one side of vane 69, causing the vanesto be rotated in a clockwise direction until it reaches stop 77. Thusthe draw bar is rotated simultaneously with the rotation of the vanes asexplained herein above.

With valve 89 being kept energized, valve 91 is deenergized allowing thefiuid to return to reservoir and the piston 37 to return to its normalposition. Thus, the tool cutter is expanded to the new adjusted radialposition. After the piston is retracted, valve 89 is deenergized causingthe uid from the chamber 65 of rotary actuator 13 to return to reservoirand the vanes 69 and 71 to return to its original position by force offluid fiowing on the other side of vanes 69 and 71. This resets therotary actuator unit to its normal position.

The foregoing cycles can be performed either manually or automaticallygenerated command signals. Moreover, it is to be understood that thedevice hereinabove described will function either rotatively or whenstationary.

What is claimed is:

1. A rotary-linear actuator adapted to retract or compensate a cuttingtool in either direction on a precision boring spindle during spindlerotation, comprising:

(A) rotatable actuator means, said rotatable actuator means comprising:

(1) a rotatable cylindrical housing, said rotatable cylindrical housinghaving;

(a) a manifold, said manifold having a bore for receiving a rotatableshaft;

(b) a cylindrical body, said cylindrical body having a bore with apiston slidably mounted therein;

(l) one end of said piston having a recessed bore extending axiallyapproximately to the midpoint of its thickness;

(2) said recessed bore having internal spline teeth thereon;

(3) first toothed clutch teeth mounted circumferentially on said one endof said piston around said recessed bore; and

(4) second toothed clutch teeth mounted circumferentially on the otherend of said piston,

(c) a rotary actuator unit; said rotary actuator unit having vane meansconnected to a sleeve having a bore; and

(d) a draw bar, said draw bar having spline teeth on one end, mounted insaid bore of said sleeve, said spline teeth on said draw bar engagingsaid interlan spline teeth of said piston;

(B) a stationary cylindrical coupling mounted on the end of saidcylindrical rotatable actuator means and having inlet and outlet fluidports connected to said rotatable shaft interconnecting said manifoldand said coupling whereby, While in motion caused by rotation of apulley means, said draw bar is adapted to be additionally moved by saidvanes in either direction, thus effecting incremental radial movement ofa tool cutter in either direction on the end of said draw bar.

References Cited UNITED STATES PATENTS 3,424,285 1/1969 McRay 192-87.17X 10 3,391,585 7/1968 Griswold 77-4 R 2,639,014 5/1953 Munschauer 19285A MARTIN P. SCHWADRON, Primary Examiner R. H. LAZARUS, AssistantExaminer U.S. C1. X.R. 77-4 R

